U.S. patent number 10,808,646 [Application Number 16/243,134] was granted by the patent office on 2020-10-20 for cooled piston and cylinder for compressors and engines.
This patent grant is currently assigned to Haier US Appliance Solutions, Inc.. The grantee listed for this patent is Haier US Appliance Solutions, Inc.. Invention is credited to Slawomir Pawel Bolek, Gregory William Hahn, Praveena Alangar Subramanya.
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United States Patent |
10,808,646 |
Subramanya , et al. |
October 20, 2020 |
Cooled piston and cylinder for compressors and engines
Abstract
Systems and compression assemblies thereof are provided. In one
example aspect, a system includes a cooling fluid circuit and a
piston slidably received within a chamber of a casing. The casing
defines an inlet passage and an outlet passage. The inlet passage
receives a cooling fluid, e.g. oil or a refrigerant, from the
cooling fluid circuit. The cooling fluid flows into the inlet
passage and downstream into an inlet groove defined by the piston
along its outer surface. The cooling fluid flows downstream to a
cooling channel defined by a piston head of the piston and
thereafter into an outlet groove defined by piston along its outer
surface. The cooling fluid then flows into outlet passage of casing
and is returned to cooling fluid circuit. The passage of cooling
fluid through the passages, grooves, and channels removes heat from
the casing and the piston.
Inventors: |
Subramanya; Praveena Alangar
(Karnataka, IN), Bolek; Slawomir Pawel (Louisville,
KY), Hahn; Gregory William (Louisville, KY) |
Applicant: |
Name |
City |
State |
Country |
Type |
Haier US Appliance Solutions, Inc. |
Wilmington |
DE |
US |
|
|
Assignee: |
Haier US Appliance Solutions,
Inc. (Wilmington, DE)
|
Family
ID: |
71404690 |
Appl.
No.: |
16/243,134 |
Filed: |
January 9, 2019 |
Prior Publication Data
|
|
|
|
Document
Identifier |
Publication Date |
|
US 20200217270 A1 |
Jul 9, 2020 |
|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04B
1/00 (20130101); F04B 39/06 (20130101); F02F
3/22 (20130101) |
Current International
Class: |
F02F
3/22 (20060101) |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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102007000652 |
|
May 2009 |
|
DE |
|
2107427 |
|
Apr 1983 |
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GB |
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2002061582 |
|
Feb 2002 |
|
JP |
|
Primary Examiner: Tran; Long T
Attorney, Agent or Firm: Dority & Manning, P.A.
Claims
What is claimed is:
1. A system, comprising: a cooling fluid circuit configured to
receive a cooling fluid; a compression assembly, comprising: a
casing defining a chamber, an inlet passage, and an outlet passage,
the inlet passage in fluid communication with the cooling fluid
circuit and configured to receive the cooling fluid, the outlet
passage in fluid communication with the cooling fluid circuit and
configured to return the cooling fluid to the cooling fluid
circuit; a piston slidably received within the chamber of the
casing, the piston having a piston head and an outer surface, the
piston head defining a cooling channel and the piston defining an
inlet groove and an outlet groove along the outer surface of the
piston, wherein the inlet groove of the piston fluidly connects the
inlet passage of the casing with the cooling channel of the piston,
and wherein the outlet groove of the piston fluidly connects the
cooling channel of the piston with the outlet passage of the
casing, wherein the piston is slidable between a top dead center
position and a bottom dead center position within the chamber of
the casing, and wherein the inlet groove of the piston fluidly
connects the inlet passage of the casing with the cooling channel
of the piston at both the top dead center position and the bottom
dead center position, and wherein the outlet groove of the piston
fluidly connects the cooling channel of the piston with the outlet
passage of the casing at both the top dead center position and the
bottom dead center position.
2. The system of claim 1, wherein a stroke of the piston is defined
between the top dead center position and the bottom dead center
position, and wherein the inlet passage of the casing has an outlet
and the outlet passage of the casing has an inlet, and wherein the
outlet of the inlet passage is axially and radially aligned with at
least a portion of the inlet groove of the piston and the inlet of
the outlet passage is axially and radially aligned with at least a
portion of the outlet groove of the piston through the stroke of
the piston.
3. The system of claim 1, wherein the piston head defines a
plurality of fins projecting into the cooling channel.
4. The system of claim 1, wherein the casing defines one or more
casing channels fluidly connecting the inlet passage with the
outlet passage of the casing.
5. The system of claim 4, wherein at least one of the one or more
casing channels extends annularly around the casing to fluidly
connect the inlet passage with the outlet passage.
6. The system of claim 1, wherein the compression assembly defines
an axial direction, a radial direction, and a circumferential
direction, and wherein the piston is slidable along a first axis
that extends along the axial direction, and wherein the cooling
channel of the piston head extends along the circumferential
direction around the first axis equal to or more than one hundred
eighty degrees (180.degree.).
7. The system of claim 1, wherein the compression assembly defines
an axial direction, a radial direction, and a circumferential
direction, and wherein the piston has a skirt having an axial
length, and wherein the inlet groove and the outlet groove extend
along the axial direction at least half the axial length of the
skirt.
8. The system of claim 1, wherein the compression assembly defines
an axial direction, a radial direction, and a circumferential
direction, and wherein the chamber of the casing has an axial
length that extends between a first end and a second end along the
axial direction, and wherein the inlet passage and the outlet
passage of the casing extend a distance that is at least half of
the axial length of the chamber along the axial direction.
9. The system of claim 1, wherein the compression assembly defines
an axial direction, a radial direction, and a circumferential
direction, and wherein the chamber extends between a first end and
a second end along the axial direction, and wherein the inlet
passage and the outlet passage of the casing each extend along the
axial direction from at least the first end of the chamber to an
axial position that is further toward the second end of the chamber
than a first surface of the piston head along the axial
direction.
10. The system of claim 1, further comprising: a temperature sensor
operable to sense an outlet temperature of the cooling fluid at the
outlet passage of the casing; a fluid control device operable to
selectively control a flow rate of the cooling fluid through the
casing and the piston; and a controller communicatively coupled
with the temperature sensor and the fluid control device, the
controller configured to: receive one or more signals indicative of
the outlet temperature of the cooling fluid at the outlet passage
of the casing; determine a first flow rate for cooling the casing
and the piston based at least in part on the one or more signals;
and control the fluid control device to selectively control the
flow rate of the cooling fluid through the casing and the piston at
the first flow rate.
11. The system of claim 1, wherein the cooling channel defined by
the piston head extends between an outer wall of the piston and a
center hub of the piston.
12. The system of claim 1, further comprising: a hermetic shell,
wherein the compression assembly and the cooling fluid circuit are
entirely encased within the hermetic shell.
13. The system of claim 1, wherein the cooling fluid is a
refrigerant.
14. A compression assembly defining an axial direction, a radial
direction, and a circumferential direction, the compression
assembly comprising: a casing defining a chamber, an inlet passage,
and an outlet passage, the inlet passage configured to receive a
cooling fluid from a cooling fluid circuit and the outlet passage
configured to return the cooling fluid to the cooling fluid
circuit; and a piston slidably received within the chamber of the
casing along the axial direction and movable between a top dead
center position and a bottom dead center position to define a
stroke of the piston, the piston having a piston head and an outer
surface, the piston head defining a cooling channel, the piston
defining an inlet groove extending longitudinally along the axial
direction at the outer surface of the piston and an outlet groove
extending longitudinally along the axial direction at the outer
surface of the piston, the inlet groove spaced from the outlet
groove along the circumferential direction, and wherein the inlet
groove of the piston fluidly connects the inlet passage of the
casing with the cooling channel of the piston through the stroke of
the piston, and wherein the outlet groove of the piston fluidly
connects the cooling channel of the piston with the outlet passage
of the casing through the stroke of the piston.
15. The compression assembly of claim 14, wherein the compression
assembly is a linear compressor of an appliance.
16. The compression assembly of claim 14, wherein the casing has an
outer surface and an inner surface radially spaced from the outer
surface, and wherein the casing defines one or more casing channels
along the outer surface, and wherein the one or more casing
channels are fluidly connected with at least one of the inlet
passage and the outlet passage, and wherein the compression
assembly further comprises: a casing cap attached to or fit over
the casing such that the one or more casing channels are
enclosed.
17. The compression assembly of claim 14, wherein the piston head
of the piston has a first wall at least partially defining the
cooling channel, and wherein the compression assembly further
comprises: a piston cap attached to the piston head and positioned
such that the piston cap is radially spaced from the first wall and
forms a second wall of the piston head to enclose the cooling
channel.
18. The compression assembly of claim 14, further comprising: a
metallic foam component disposed in at least one of the cooling
channel, the inlet passage, and the outlet passage.
Description
FIELD OF THE INVENTION
The present subject matter relates generally to piston and cylinder
arrangements having cooling features for compressors and
reciprocating engines.
BACKGROUND OF THE INVENTION
Refrigerator appliances generally include a compressor. During
operation of the refrigerator appliance, the compressor operates to
provide compressed refrigerant. The refrigerator appliance utilizes
such compressed refrigerant to cool a compartment of the appliance
and food items located therein. Recently, linear compressors have
been used to compress refrigerant in refrigerator appliances.
Linear compressors can include a piston slidably received within a
chamber of a cylinder. The piston is slid backward and forwards
within the chamber to compress refrigerant. Valves positioned in a
cylinder head of the cylinder may allow for ingress and egress of
the refrigerant into and from the chamber.
At the end of a compression phase or stroke of the compression
process, the cylinder and valve temperatures are typically near the
discharge temperature of the compressed gaseous refrigerant. The
direction of heat transfer may change during the compression
process depending on the gas temperature inside the cylinder. For
instance, when the gas temperature is lower than the temperature of
the cylinder walls, heat flux is positive and heat is transferred
from the cylinder walls to the gaseous refrigerant. When the
gaseous refrigerant reaches the same temperature as the cylinder
walls, heat flux is zero. When the gas temperature is greater than
the temperature of the cylinder walls, heat flux is negative and
heat is transferred from the gaseous refrigerant to the cylinder
walls. The change in direction of heat transfer occurs not just
during the compression phase, but also during the expansion phase
or stroke of the compression process.
In some instances, the high discharge temperature of the gaseous
refrigerant heats the cylinder walls and causes superheating of the
gaseous refrigerant in the cylinder, resulting in a decrease in
compressor efficiency. The magnitude of the decrease in compressor
efficiency is mostly determined by the cylinder wall temperature.
Moreover, many conventional compressors operate closely or as near
as possible to isentropic compression. While operating the
compressor close to isentropic compression prevents certain issues
commonly associated with more efficient processes, e.g., wet
compression, isentropic compression is not as efficient as other
compression processes, such as e.g., isothermal compression.
Accordingly, conventional compressors are typically not operated
using compression processes that maximize compressor
efficiency.
Accordingly, systems and compression assemblies thereof that
address one or more of the challenges noted above would be
useful.
BRIEF DESCRIPTION OF THE INVENTION
Aspects and advantages of the invention will be set forth in part
in the following description, or may be apparent from the
description, or may be learned through practice of the
invention.
In one example embodiment, a system is provided. The system
includes a cooling fluid circuit configured to receive a cooling
fluid. The system also includes a compression assembly. The
compression assembly includes a casing defining a chamber, an inlet
passage, and an outlet passage, the inlet passage in fluid
communication with the cooling fluid circuit and configured to
receive the cooling fluid, the outlet passage in fluid
communication with the cooling fluid circuit and configured to
return the cooling fluid to the cooling fluid circuit. Further, the
compression assembly includes a piston slidably received within the
chamber of the casing, the piston having a piston head and an outer
surface, the piston head defining a cooling channel and the piston
defining an inlet groove and an outlet groove along the outer
surface of the piston, wherein the inlet groove of the piston
fluidly connects the inlet passage of the casing with the cooling
channel of the piston, and wherein the outlet groove of the piston
fluidly connects the cooling channel of the piston with the outlet
passage of the casing.
In another example embodiment, a compression assembly defining an
axial direction, a radial direction, and a circumferential
direction is provided. The compression assembly includes a casing
defining a chamber, an inlet passage, and an outlet passage, the
inlet passage configured to receive a cooling fluid from a cooling
fluid circuit and the outlet passage configured to return the
cooling fluid to the cooling fluid circuit. Further, the
compression assembly includes a piston slidably received within the
chamber of the casing along the axial direction and movable between
a top dead center position and a bottom dead center position to
define a stroke of the piston, the piston having a piston head and
an outer surface, the piston head defining a cooling channel, the
piston defining an inlet groove extending longitudinally along the
axial direction at the outer surface of the piston and an outlet
groove extending longitudinally along the axial direction at the
outer surface of the piston, the inlet groove spaced from the
outlet groove along the circumferential direction. The inlet groove
of the piston fluidly connects the inlet passage of the casing with
the cooling channel of the piston through the stroke of the piston,
and wherein the outlet groove of the piston fluidly connects the
cooling channel of the piston with the outlet passage of the casing
through the stroke of the piston.
These and other features, aspects and advantages of the present
invention will become better understood with reference to the
following description and appended claims. The accompanying
drawings, which are incorporated in and constitute a part of this
specification, illustrate embodiments of the invention and,
together with the description, serve to explain the principles of
the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
A full and enabling disclosure of the present invention, including
the best mode thereof, directed to one of ordinary skill in the
art, is set forth in the specification, which makes reference to
the appended figures, in which:
FIG. 1 provides a front view of a refrigerator appliance according
to an example embodiment of the present subject matter;
FIG. 2 provides a schematic view of a refrigeration system of the
refrigerator appliance of FIG. 1;
FIG. 3 provides a schematic view of a linear compressor according
to an example embodiment of the present subject matter;
FIG. 4 provides a close up, schematic view of a piston slidably
received within a chamber of a casing of the linear compressor of
FIG. 3 and positioned in a top dead center position according to an
example embodiment of the present subject matter;
FIG. 5 provides a schematic view of the piston of FIG. 4 slidably
received within the chamber and positioned in a bottom dead center
position;
FIG. 6 provides a perspective view of an example piston according
to an example embodiment of the present subject matter;
FIG. 7 provides a perspective, cross-sectional view of the piston
of FIG. 6 taken along line 7-7 of FIG. 6;
FIG. 8 provides a perspective, cross-sectional view of the piston
of FIG. 6 taken along line 8-8 of FIG. 6;
FIGS. 9 and 10 provide perspective, cross sectional views of the
piston of FIGS. 6 through 8 slidably received within the chamber of
the casing according to an example embodiment of the present
subject matter;
FIGS. 11 through 13 provide various perspective views of another
example piston according to an example embodiment of the present
subject matter;
FIG. 14 provides a close up, schematic view of a piston slidably
received within a chamber of a casing of an example compression
assembly according to an example embodiment of the present subject
matter;
FIG. 15 provides a schematic cross-sectional view of a piston
slidably received within a chamber of a casing of an example
compression assembly according to an example embodiment of the
present subject matter; and
FIG. 16 provides a schematic view of another linear compressor
according to an example embodiment of the present subject
matter.
DETAILED DESCRIPTION
Reference now will be made in detail to embodiments of the
invention, one or more examples of which are illustrated in the
drawings. Each example is provided by way of explanation of the
invention, not limitation of the invention. In fact, it will be
apparent to those skilled in the art that various modifications and
variations can be made in the present invention without departing
from the scope or spirit of the invention. For instance, features
illustrated or described as part of one embodiment can be used with
another embodiment to yield a still further embodiment. Thus, it is
intended that the present invention covers such modifications and
variations as come within the scope of the appended claims and
their equivalents.
As used herein, terms of approximation, such as "approximately,"
"substantially," or "about," refer to being within a ten percent
(10%) margin of error of the stated value. Moreover, as used
herein, the terms "first", "second", and "third" may be used
interchangeably to distinguish one component from another and are
not intended to signify location or importance of the individual
components. The terms "upstream" and "downstream" refer to the
relative direction with respect to fluid flow in a fluid pathway.
For example, "upstream" refers to the direction from which the
fluid flows, and "downstream" refers to the direction to which the
fluid flows.
FIG. 1 provides a refrigerator appliance 10 that incorporates a
sealed refrigeration system 60 (FIG. 2). It should be appreciated
that the term "refrigerator appliance" is used in a generic sense
herein to encompass any manner of refrigeration appliance, such as
a freezer, refrigerator/freezer combination, and any style or model
of conventional refrigerator. In addition, it should be understood
that the present subject matter is not limited to use in
appliances. Thus, the present subject matter may be used for any
other suitable purpose, such as vapor compression within air
conditioners or heat pumps, air compressors, as well as to
reciprocating engine applications.
In the illustrated example embodiment shown in FIG. 1, refrigerator
appliance 10 is depicted as an upright refrigerator having a
cabinet or casing 12 that defines a number of internal storage
compartments. In particular, refrigerator appliance 10 includes
upper fresh food compartments 14 having doors 16 and lower freezer
compartment 18 having upper drawer 20 and lower drawer 22. The
drawers 20, 22 may be "pull-out" drawers in that they can be
manually moved into and out of the freezer compartment 18 on
suitable slide mechanisms.
FIG. 2 provides a schematic view of refrigerator appliance 10
including an example system 60, which is a sealed refrigeration
system in the depicted embodiment of FIG. 2. As shown, a machinery
compartment 62 contains components for executing a vapor
compression cycle for cooling air within refrigerator appliance 10.
Sealed refrigeration system 60 includes a compression assembly,
which is a linear compressor 100 in the depicted embodiment of FIG.
2. Sealed refrigeration system 60 also includes a condenser 66, an
expansion device 68, and an evaporator 70 connected in series and
charged with a refrigerant. For this embodiment, sealed
refrigeration system 60 also includes a suction line heat exchanger
(SLHX) 74. As will be understood by those skilled in the art,
refrigeration system 60 may include additional components, e.g., at
least one additional evaporator, compressor, expansion device,
and/or condenser. As an example, refrigeration system 60 may
include two evaporators.
Within refrigeration system 60, gaseous refrigerant flows into
linear compressor 100, which operates to increase the pressure of
the refrigerant. The compression of the refrigerant raises its
temperature, which is lowered by passing the gaseous refrigerant
through condenser 66. Within condenser 66, heat exchange with
ambient air takes place so as to cool the refrigerant and cause the
refrigerant to condense to a liquid state. A fan 72 is used to move
air across condenser 66, as illustrated by arrows A.sub.C, so as to
provide forced convection for a more rapid and efficient heat
exchange between the refrigerant within condenser 66 and the
ambient air. Thus, as will be understood by those skilled in the
art, increasing air flow across condenser 66 can, e.g., increase
the efficiency of condenser 66 by improving cooling of the
refrigerant contained therein.
An expansion device (e.g., a valve, capillary tube, or other
restriction device) 68 receives liquid refrigerant from condenser
66. From expansion device 68, the liquid refrigerant enters
evaporator 70. Upon exiting expansion device 68 and entering
evaporator 70, the liquid refrigerant drops in pressure and
temperature. Due to the pressure drop and phase change of the
refrigerant, evaporator 70 is cool relative to compartments 14, 18
of refrigerator appliance 10. As such, cooled air is produced and
refrigerates compartments 14, 18 of refrigerator appliance 10.
Thus, evaporator 70 is a type of heat exchanger that transfers heat
from air passing over evaporator 70 to refrigerant flowing through
evaporator 70. SLHX 74 superheats the vapor in the gaseous
refrigerant that has exited evaporator 70 and subcools the liquid
refrigerant that has exited condenser 66.
As further depicted in FIG. 2, system 60 includes a cooling fluid
circuit 80. A volume of cooling fluid (e.g., refrigerant) may be
circulated along cooling fluid circuit 80 and downstream to a heat
exchanger 140 of linear compressor 100. As will be explained in
detail below, heat exchanger 140 of linear compressor 100 is
operable to cool a cylinder and piston of linear compressor 100 to
ultimately improve the performance of linear compressor 100 and to
reduce the thermodynamic work required for compression of the
gaseous refrigerant.
For this embodiment, an amount of liquid refrigerant from the vapor
compression cycle may be diverted into cooling fluid circuit 80.
Particularly, a volume of liquid refrigerant may be diverted into
cooling fluid circuit 80 downstream of an outlet of condenser 66
and upstream of expansion device 68 as shown in FIG. 2. In some
alternative embodiments, liquid refrigerant may be diverted into
cooling fluid circuit 80 downstream of expansion device 68 and
upstream of evaporator 70. A fluid control device 82 is positioned
along cooling fluid circuit 80 and is operable to selectively
control a flow rate of the cooling fluid (e.g., refrigerant)
through cooling fluid circuit 80. For the depicted embodiment of
FIG. 2, fluid control device 82 is a solenoid valve. However, in
other embodiments, fluid control device 82 may be another suitable
type of valve or device capable of selectively controlling the flow
rate of the cooling fluid through cooling fluid circuit 80. As
further shown in FIG. 2, a capillary tube 84 may optionally be
positioned along cooling fluid circuit 80, e.g., for further
metering the flow rate of the cooling fluid flowing through cooling
fluid circuit 80. Thus, the flow rate of the cooling fluid (e.g.,
liquid refrigerant) diverted into cooling fluid circuit 80 may be
controlled by fluid control device 82 and may be further metered by
capillary tube 84 before flowing downstream to heat exchanger 140
of linear compressor 100 and eventually back through condenser
66.
Refrigerator appliance 10 includes various temperature sensors. For
this embodiment, system 60 of refrigerator appliance 10 includes a
temperature sensor 86 operable to sense an outlet temperature of
the cooling fluid (e.g., the liquid refrigerant) at the outlet of
linear compressor 100, or more particularly, at an outlet passage
defined by a cylinder of linear compressor 100 as will be explained
further below. Refrigerator appliance 10 also includes a
compartment temperature sensor 88 operable to sense a temperature
of the air within one or more chilled chambers of refrigerator
appliance 10, e.g., fresh food and freezer compartments 14, 18. In
some embodiments, refrigerator appliance 10 may include multiple
compartment temperature sensors. For instance, refrigerator
appliance 10 may include one or more compartment temperature
sensors for sensing the air within fresh food compartment 14 and
one or more compartment temperature sensors for sensing the air
within freezer compartment 18. Temperature sensor 86 and
compartment temperature sensor(s) 88 may be any suitable type of
temperature sensors.
Refrigerator appliance 10 includes a controller 90. Controller 90
is communicatively coupled with various components of refrigerator
appliance 10, including but not limited to, fluid control device
82, temperature sensor 86, compartment temperature sensor 88, fan
72 (or an electric motor thereof), expansion device 68, the fan of
evaporator 70 (or an electric motor thereof), etc. Control signals
generated in or by controller 90 operate refrigerator appliance 10,
including various components of system 60, such as e.g., the
components listed above. As used herein, controller 90 may refer to
one or more microprocessors or semiconductor devices and is not
restricted necessarily to a single element. The processing device
can be programmed to operate refrigerator appliance 10. The
processing device may include, or be associated with, one or more
memory elements (e.g., non-transitory storage media). In some such
embodiments, the memory elements include electrically erasable,
programmable read only memory (EEPROM). Generally, the memory
elements can store information accessible processing device,
including instructions that can be executed by processing device.
Optionally, the instructions can be software or any set of
instructions and/or data that when executed by the processing
device, cause the processing device to perform operations.
Collectively, the vapor compression cycle components in a
refrigeration circuit, associated fans, and associated compartments
are sometimes referred to as a sealed refrigeration system operable
to force cold air through refrigeration compartments 14, 18. The
refrigeration system 60 depicted in FIG. 2 is provided by way of
example only. Thus, it is within the scope of the present subject
matter for other configurations of the refrigeration system to be
used as well.
FIG. 3 provides a schematic view of linear compressor 100 according
to an example embodiment of the present subject matter. As shown in
FIG. 3, linear compressor 100 is enclosed in a hermetic or airtight
shell 104. Hermetic shell 104 can, e.g., hinder or prevent
refrigerant from leaking or escaping from refrigeration system 60
(FIG. 2) at linear compressor 100. Hermetic shell 104 may be a
metal hermetic shell or may be constructed of or with any suitable
type of metal, such as steel. Linear compressor 100 defines an
axial direction A, a radial direction R, and a circumferential
direction C that extends three hundred sixty degrees (360.degree.)
around the axial direction A.
Linear compressor 100 includes a cylinder or casing 110 enclosed
within hermetic shell 104. Casing 110 defines a chamber 112 that
extends longitudinally along the axial direction A. Casing 110
further includes valves that permit refrigerant (shown as "R") to
enter and exit chamber 112 during compression of the refrigerant R
by linear compressor 100. Linear compressor 100 further includes a
piston 120 slidably received within chamber 112 of casing 110. In
particular, piston 120 is movable or slidable along a first axis A1
between a top dead center position (FIG. 3) and a bottom dead
center position (FIG. 4). The first axis A1 extends along the axial
direction A. Piston 120 may assume a default position, e.g., when
linear compressor 100 is not in operation. Piston 120 has a piston
head 122 and a skirt 124 extending from piston head 122, e.g.,
longitudinally along the axial direction A. During sliding of
piston 120 within chamber 112, piston 120 compresses refrigerant R
within chamber 112.
Piston 120 is coupled with a drive assembly 128 via a connecting
rod 126. Drive assembly 128 is operable to move or reciprocate
piston 120 along the axial direction A within chamber 112. In some
example embodiments, drive assembly 128 includes a motor (not
shown) with at least one driving coil (not shown). The driving coil
is configured for selectively urging piston 120 to slide along the
axial direction A within chamber 112. In particular, the driving
coil receives a current from a power supply (not shown) in order to
generate a magnetic field that engages a magnet and urges piston
120 to move along the axial direction A in order to compress
refrigerant R within chamber 112, as will be understood by those
skilled in the art. In particular, the driving coil can slide
piston 120 between the top dead center position and the bottom dead
center position.
As an example, from the top dead center position, piston 120 can
slide within chamber 112 towards the bottom dead center position
along the axial direction A, i.e., an expansion stroke of piston
120. During the expansion stroke of piston 120, an intake/suction
valve 130 permits refrigerant R to enter chamber 112.
Intake/suction valve 130 is housed within a cylinder or casing head
114 of casing 110. When piston 120 reaches the bottom dead center
position, piston 120 changes direction and slides in chamber 112
back towards the top dead center position, i.e., a compression
stroke of piston 120. During the compression stroke of piston 120,
refrigerant R that enters chamber 112 during the expansion stroke
is compressed until refrigerant R reaches a particular pressure.
The compressed refrigerant R, now at a higher pressure and
temperature, exits chamber 112 through a discharge valve 132. In
such a manner, refrigerant R is compressed within chamber 112 by
piston 120. Discharge valve 132 is housed in casing head 114
adjacent intake/suction valve 130.
During operation of linear compressor 100, piston 120 reciprocates
to compress refrigerant R, and the compressed refrigerant R flows
out of chamber 112 through discharge valve 132. From discharge
valve 132, the compressed refrigerant R is directed into a
discharge conduit 134. Discharge conduit 134 extends between
discharge valve 132 and hermetic shell 104 such that the compressed
refrigerant R is flowable through discharge conduit 134 from
discharge valve 132 to hermetic shell 104. Refrigerant R flowing
downstream through discharge conduit 134 may be a liquid
refrigerant and may flow downstream to condenser 66 (FIG. 2).
Discharge conduit 134 may be plastic tubing suitable for use with a
refrigerant. For example, discharge conduit 134 may be
polytetrafluoroethylene plastic tubing, polyethylene plastic
tubing, or nylon plastic tubing.
As further shown in FIG. 3, linear compressor 100 includes heat
exchanger 140. Heat exchanger 140 is formed by various passages,
grooves, and channels defined by casing 110 and piston 120 that are
each configured to receive a cooling fluid, such as e.g.,
refrigerant from cooling fluid circuit 80, oil from a lubrication
circuit, or some other suitable cooling fluid. For this embodiment,
the cooling fluid CF is refrigerant R that is diverted from into
cooling fluid circuit 80 as described above. Particularly, the
cooling fluid CF circulated through cooling fluid circuit 80 (FIG.
2) flows through casing 110 and piston 120 to ultimately cool
casing 110 and piston 120, which as noted above, may provide
improved compressor performance and reduce the thermodynamic work
required for compression of the gaseous refrigerant.
FIG. 4 provides a close up, schematic view of piston 120 slidably
received within chamber 112 of casing 110 at the bottom dead center
position according to an example embodiment of the present subject
matter. Moreover, FIG. 4 depicts a close up view of heat exchanger
140. As shown, casing 110 defines an inlet passage 142 in fluid
communication with the cooling fluid circuit 80. Inlet passage 142
extends between an inlet 146 and an outlet 148. Inlet 146 of inlet
passage 142 is in fluid communication with cooling fluid circuit 80
(FIG. 2). Notably, outlet 148 of inlet passage 142 is defined at an
inner surface 116 of casing 110 that at least partially defines
chamber 112. Casing 110 also defines an outlet passage 144 in fluid
communication with the cooling fluid circuit 80. Outlet passage 144
extends between an inlet 150 and an outlet 152. As depicted, inlet
150 of outlet passage 144 is defined at inner surface 116 of casing
110 that at least partially defines chamber 112. Outlet 152 of
outlet passage 144 is in fluid communication with cooling fluid
circuit 80 (FIG. 3).
Further, piston 120 defines a cooling channel 154, an inlet groove
156, and an outlet groove 158. More particularly, piston head 122
defines cooling channel 154 and inlet groove 156 and outlet groove
158 are defined by piston 120 along an outer surface 125 of piston
120. Inlet groove 156 and outlet groove 158 are spaced from one
another, e.g., along the circumferential direction C, and both
extend longitudinally along the axial direction A. Inlet groove 156
is defined axially along at least a portion of piston head 122 and
along at least a portion of skirt 124 at outer surface 125 of
piston 120. Similarly, outlet groove 158 is defined axially along
at least a portion of piston head 122 and along at least a portion
of skirt 124 at outer surface 125 of piston 120. Inlet groove 156
of piston 120 fluidly connects inlet passage 142 of casing 110 with
cooling channel 154 of piston 120. Outlet groove 158 of piston 120
fluidly connects cooling channel 154 of piston 120 with outlet
passage 144 of casing 110. Accordingly, the cooling fluid CF (e.g.,
refrigerant, oil, etc.) may flow through inlet passage 142 of
casing 110 and into inlet groove 156 of skirt 124 of piston 120,
through cooling channel 154 of piston head 122, along outlet groove
158 of skirt 124, and may flow out of heat exchanger 140 through
outlet passage 144 of casing 110 where the cooling fluid CF may
return to cooling fluid circuit 80 and flow downstream to condenser
66 (FIG. 2).
Notably, as shown in FIGS. 3 and 4, inlet groove 156 fluidly
connects inlet passage 142 of casing 110 with cooling channel 154
at both the top dead center position (FIG. 3) and the bottom dead
center position (FIG. 4). Moreover, outlet groove 158 fluidly
connects cooling channel 154 with outlet passage 144 of casing 110
at both the top dead center position (FIG. 3) and the bottom dead
center position (FIG. 4). Stated another way, outlet 148 of inlet
passage 142 is axially and radially aligned with at least a portion
of inlet groove 156 defined by piston 120 and inlet 150 of outlet
passage 144 is axially and radially aligned with at least a portion
of outlet groove 158 of piston 120 through the stroke of piston 120
between its top dead center and bottom dead center positions. In
such a manner, a continuous flow of cooling fluid CF may circulate
through heat exchanger 140, which may prevent or reduce sloshing of
the cooling fluid CF as piston 120 reciprocates and may also
provide enhanced cooling as cooling fluid CF may be continuously
circulated through heat exchanger 140, among other benefits and
advantages.
As further shown in FIG. 4, chamber 112 of casing 110 has an axial
length L.sub.C that extends between a first end 113 and a second
end 115 of chamber 112 along the axial direction A. As depicted,
inlet passage 142 defined by casing 110 extends a distance along
the axial direction A that is at least half of the axial length
L.sub.C of chamber 112. In a similar manner, outlet passage 144
defined by casing 110 extends a distance along the axial direction
A that is at least half of the axial length L.sub.C of chamber 112.
In this manner, cooling fluid CF may provide enhanced cooling to
casing 110 and may ultimately reduce the discharge temperature of
the gaseous refrigerant. In some embodiments, inlet passage 142
extends axially at least from first end 113 of chamber 112 to an
axial position that is further towards second end 115 of chamber
112 than a top or first surface 127 of piston head 122 of piston
120 along the axial direction A. In this way, cooling fluid CF
passing through inlet passage 142 and outlet passage 144 may cool
casing 110 along the entire axial length in which gaseous
refrigerant may contact annular inner surface 116 of casing
110.
FIG. 5 provides a schematic view of piston 120 slidably received
within chamber 112 of casing 110 and positioned in a bottom dead
center position. As shown, for this embodiment, casing 110 defines
one or more casing channels fluidly connecting inlet passage 142 of
casing 110 with outlet passage 144 of casing 110. Particularly,
casing 110 defines a first casing channel 181 extending annularly
around chamber 112 and fluidly connecting inlet passage 142 with
outlet passage 144, a second casing channel 182 extending annularly
around chamber 112 and fluidly connecting inlet passage 142 with
outlet passage 144, and a third casing channel 183 extending
annularly around chamber 112 and fluidly connecting inlet passage
142 with outlet passage 144. Casing channels 181, 182, 182 are
spaced from one another, e.g., along the axial direction A, and are
fluidly connected to one another by an axial section 143 of inlet
passage 142 that extends longitudinally along the axial direction A
as well as by an axial section 145 of outlet passage 144 that
extends longitudinally along the axial direction A. Generally
casing channels 181, 182, 183 are configured to receive cooling
fluid CF and thus casing channels 181, 182, 183 provide cooling
circumferentially around chamber 112, e.g. at various axial
positions as shown in FIG. 5. Although three (3) casing channels
are depicted in FIG. 5, it will be appreciated that casing 110 may
define more or less than three (3) casing channels 181, 182,
183.
Further in some embodiments, casing 110 may define one or more
axial casing channels that extend axially between one or more
casing channels. For instance, a first axial casing channel may
extend axially between and fluidly connect first casing channel
181, second casing channel 182, and third casing channel 183.
Further, a second first axial casing channel may extend axially
between and fluidly connect first casing channel 181, second casing
channel 182, and third casing channel 183, and may be positioned
radially opposite the first casing channel 181 (i.e., the first
axial casing channel may be spaced one hundred eighty degrees
(180.degree.) from the second axial casing channel). In such
embodiments, the first axial casing channel may be spaced
circumferentially from inlet passage 142 by ninety degrees
(90.degree.), and consequently, the second axial casing channel may
be spaced circumferentially from outlet passage 144 by ninety
degrees (90.degree.). Moreover, in some embodiments, casing 110 may
define a single annular casing channel that extends three hundred
sixty degrees (360.degree.) around chamber 112. In such
embodiments, inlet passage 142 includes inlet 146 and outlet 148
but the axial portion of inlet passage 142 may be integrated with
the annular casing channel. Likewise, outlet passage 144 includes
inlet 150 and outlet 152 but the axial portion of outlet passage
144 may be integrated with the annular casing channel.
In addition, in some alternative embodiments, casing 110 defines
inlet passage 142 and outlet passage 144 as a radial hole through
casing 110. In such embodiments, casing 110 defines inlet passage
142 and outlet passage 144 without an axial section that extends
longitudinally along the axial direction A (e.g., without axial
sections 143, 145). Further, in some embodiments, casing 110 need
not define casing channels and may only include a cooling fluid
ingress (e.g., a radial hole) and a cooling fluid egress from
piston 120.
FIGS. 6, 7, and 8 provide various views of piston 120 according to
an example embodiment of the present subject matter. In particular,
FIG. 6 provides a perspective view of piston 120, FIG. 7 provides a
perspective, cross-sectional view of piston 120 depicting piston
120 sectioned along line 7-7 of FIG. 6, and FIG. 8 provides a
perspective, cross-sectional view of piston 120 depicting piston
120 sectioned along line 8-8 of FIG. 6.
As shown, inlet groove 156 is defined along outer surface 125 of
piston 120. Inlet groove 156 has a groove width W1, a groove length
L1 (FIG. 8), and a groove depth D1. The groove width W1 of inlet
groove 156 extends along the circumferential direction C, the
groove length L1 of inlet groove 156 extends along the axial
direction A, and the groove depth D1 extends along the radial
direction R. Generally, inlet groove 156 extends longitudinally
along the axial direction A and is recessed or undercut into outer
surface 125 of piston 120. Inlet groove 156 extends axially along
at least a portion of piston head 122 and along at least a portion
of skirt 124 at outer surface 125 of piston 120.
Outlet groove 158 is configured in a similar manner as inlet groove
156. That is, outlet groove 158 is defined along outer surface 125
of piston 120. Outlet groove 158 has a groove width W2 (FIG. 7), a
groove length L2 (FIG. 8), and a groove depth D2 (FIG. 7). The
groove width W2 of outlet groove 158 extends along the
circumferential direction C, the groove length L2 of outlet groove
158 extends along the axial direction A, and the groove depth D2
extends along the radial direction R. Further, as shown, inlet
groove 156 and outlet groove 158 are spaced from one another along
the circumferential direction C.
Generally, outlet groove 158 extends longitudinally along the axial
direction A and is recessed or undercut into outer surface 125 of
piston 120. Inlet groove 156 extends axially along at least a
portion of piston head 122 and along at least a portion of skirt
124 at outer surface 125 of piston 120. As shown best in FIG. 8,
piston 120 extends between a first end 164 and a second end 166
along the axial direction A. Skirt 124 of piston 120 has an axial
length L.sub.S that extends between a bottom surface of second wall
123 and bottom end 166 of piston 120. Inlet groove 156 and outlet
groove 158 extend along the axial direction A at least half the
axial length L.sub.S of skirt 124. In this manner, outlet 148 of
inlet passage 142 may be fluidly connected to inlet groove 156 of
piston 120 no matter the axial position of piston 120 within
chamber 112 and inlet 150 of outlet passage 144 may be fluidly
connected to outlet groove 158 of piston 120 no matter the axial
position of piston 120 within chamber 112.
As shown best in FIGS. 7 and 8, inlet groove 156 is fluidly
connected with cooling channel 154, e.g., at an inlet of cooling
channel 154, and outlet groove 158 is fluidly connected with
cooling channel 154, e.g., at an outlet of cooling channel 154.
Generally, cooling channel 154 is defined by piston head 122. More
particularly, cooling channel 154 is defined between a first wall
121 (FIG. 8) and a second wall 123 of piston head 122, e.g., along
the axial direction A. First wall 121 is spaced from second wall
123, e.g., along the axial direction A. Cooling channel 154 has a
width W3 that extends along the radial direction R between an outer
wall 160 (FIG. 7) of piston 120 and a center hub 162. Center hub
162 has a coupling 168 (FIG. 8) extending axially toward second end
166 of piston 120 and defines a counter bore 170 extending
longitudinally along the axial direction A. Coupling 168 is
configured for receiving connecting rod 126 (FIGS. 3 and 4). Piston
head 122 of piston 120 also defines a suction port 172 extending
therethrough along the axial direction A between first wall 121 and
second wall 123.
Cooling channel 154 has a depth D3 that extends between first wall
121 and second wall 123 along the axial direction A. Cooling
channel 154 extends between inlet groove 156 and outlet groove 158.
For this embodiment, cooling channel 154 extends circumferentially
around the first axis A1 to connect inlet and outlet grooves 156,
158. For the depicted embodiment of FIG. 7, cooling channel 154 of
piston 120 extends along the circumferential direction C around the
first axis A1 equal to or more than one hundred eighty degrees
(180.degree.). Cooling channel 154 extends generally radially
opposite suction port 172 as shown in FIG. 7. In some embodiments,
piston head 122 may not define a suction port and thus may define
cooling channel 154 such that cooling channel 154 extends annularly
around first axis A1.
FIGS. 9 and 10 provide perspective, cross sectional views of piston
120 of FIGS. 6 through 8 slidably received within chamber 112 of
casing 110 according to an example embodiment of the present
subject matter. In FIG. 9, piston 120 is shown in the top dead
center position. In FIG. 10, piston 120 is shown in the bottom dead
center position. An exemplary manner in which heat generated during
the compression process may be removed from casing 110 and piston
120 by heat exchanger 140 (FIG. 4) will now be described.
With general reference to FIGS. 9 and 10, cooling fluid CF (e.g.,
refrigerant, oil, etc.) may flow from cooling fluid circuit 80
(FIG. 2) into inlet passage 142 defined by casing 110 as shown in
FIGS. 9 and 10. The cooling fluid CF extracts heat from the
relatively hot walls of casing 110 as the cooling fluid CF passes
through inlet passage 142. In some embodiments, such as the
embodiment shown in FIGS. 9 and 10, the cooling fluid CF may flow
annularly around chamber 112 via an annular casing channel 180.
Annular casing channel 180 fluidly connects inlet passage 142 and
outlet passage 144 and is integral therewith. As the cooling fluid
CF passes through annular casing channel 180, the cooling fluid CF
may extract heat from the relatively hot walls of casing 110. Some
amount of cooling fluid CF flows from inlet passage 142 into inlet
groove 156 defined along or recessed within outer surface 125 of
piston 120. As noted above, outlet 148 of inlet passage 142 is
fluidly connected with inlet groove 156 of piston 120 regardless of
the axial position of piston 120 within chamber 112. The cooling
fluid CF flows into inlet groove 156 and extracts heat from skirt
124 of piston 120 and inner surface 116 of casing 110 as piston 120
reciprocates within chamber 112. The cooling fluid CF continues
downstream into cooling channel 154 defined by piston head 122 of
piston 120. The cooling fluid CF flows generally circumferentially
through cooling channel 154 and extracts heat from the various
walls of piston head 122. Importantly, the cooling fluid CF
extracts heat from first wall 121 piston head 122, which is the
lead wall of piston 120 that interacts with the gaseous refrigerant
within chamber 112. In some embodiments, cooling channel 154
defined by piston head 122 is radially and circumferentially
aligned (at least in part) with discharge valve 132 (FIG. 3) for
improved cooling of the area of piston 120 that forces compressed
gaseous refrigerant into discharge conduit 134 (FIG. 3) through
discharge valve 132.
The cooling fluid CF exits cooling channel 154 defined by piston
head 122 and flows downstream into outlet groove 158. The cooling
fluid CF extracts heat from skirt 124 of piston 120 and inner
surface 116 of casing 110 as piston 120 reciprocates within chamber
112. The cooling fluid CF continues downstream and enters outlet
passage 144 through inlet 150 of outlet passage 144. As noted
above, inlet 150 of outlet passage 144 is fluidly connected with
outlet groove 158 regardless of the axial position of piston 120
within chamber 112. The cooling fluid CF flowing from outlet groove
158 through inlet 150 may mix with the cooling fluid flowing
annularly around chamber 112 through annular casing channel 180.
The mixed cooling fluid CF returns to cooling fluid circuit 80
(FIG. 2). For instance, the cooling fluid CF may return directly to
a main conduit of refrigeration system 60 (FIG. 2) upstream of
condenser 66 (FIG. 2) and downstream of the compressor 100 (FIG.
2), or alternatively, the cooling fluid may be directed to
discharge conduit 134 (as shown by the dotted lines in FIG. 3)
where the cooling fluid CF may mix with the compressed gaseous
refrigerant exiting linear compressor 100 through hermetic shell
104.
Extracting heat generated during the compression process in the
manner described above provides a number of advantages and
benefits. For instance, the removal or extraction of heat from
casing 110 and piston 120 reduces the discharge temperature of the
gaseous refrigerant or oil compressed within the chamber. Further,
the removal of heat moves the compression process toward a more
isothermal process, and consequently, this reduces the
thermodynamic work required for compression. Additional advantages
and benefits not specifically listed may be realized or
achieved.
In some embodiments, with reference to FIGS. 2 and 3, the flow rate
of the cooling fluid CF through heat exchanger 140 may be
controlled to remove heat from casing 110 and piston 120 whilst
accommodating the cooling needs of compartments 14, 18. In such
embodiments, controller 90 is configured to receive one or more
signals indicative of the temperature of the cooling fluid CF at an
outlet of linear compressor 100 or a position downstream of the
outlet of linear compressor 100 and upstream of condenser 66. For
instance, the signals may be indicative of the temperature of the
cooling fluid CF within outlet passage 144 (FIG. 4). For instance,
controller 90 may receive the one or more signals from temperature
sensor 86. Further, in some embodiments, controller 90 is
configured to receive one or more compartment temperature signals
indicative of the temperature of the air within one or more
compartments 14, 18 of refrigerator appliance 10. Controller 90 may
receive the one or more compartment temperature signals from
compartment temperature sensor 88, for example.
In addition, controller 90 is configured to determine a first flow
rate for delivering the cooling fluid to piston 120 and casing 110
based at least in part on the one or more signals received from
temperature sensor 86 and the one or more compartment temperature
signals received from compartment temperature sensor 88. Moreover,
controller 90 is configured to control fluid control device 82 to
selectively control the flow rate of the cooling fluid through
piston 120 and casing 110 at the first flow rate. In this way, the
volume or amount of refrigerant delivered to heat exchanger 140 may
be controlled, and consequently, the amount of cooling provided to
piston 120 and casing 110 whilst ensuring that the temperature
needs of compartments 14 and 18 are met.
FIGS. 11, 12, and 13 provide various views of another example
piston 200 according to an example embodiment of the present
subject matter. In particular, FIG. 11 provides a perspective view
of piston 200. FIG. 12 provides a perspective, cross-sectional view
of piston 200. FIG. 13 provides a perspective view of piston 200
with a second wall 212 of a piston head 206 of piston 200 removed
for illustrative purposes. Piston 200 of FIGS. 11 through 13 may be
employed with the compression assemblies and systems described
herein, such as linear compressor 100 illustrated in FIG. 3. As
shown, piston 200 extends between a first end 202 and a second end
204 along the axial direction A. Piston 200 has piston head 206
positioned generally at first end 202 and a skirt 208 extending
from piston head 206 to second end 204 of piston 200, e.g.,
longitudinally along the axial direction A. During sliding of
piston 200 within a chamber, piston 200 may compress a refrigerant
or fuel source.
As best shown in FIGS. 12 and 13, piston 200 defines a cooling
channel 214, an inlet groove 220, and an outlet groove 222. More
particularly, piston head 206 defines cooling channel 214, and
inlet groove 220 and outlet groove 222 are defined by piston 200
along an outer surface 228 of piston 200. Inlet groove 220 and
outlet groove 222 are spaced from one another, e.g., along the
circumferential direction C, and both extend longitudinally along
the axial direction A. For this embodiment, inlet groove 220 is
defined radially opposite of outlet groove 222 (i.e., inlet groove
220 is spaced from outlet groove 222 one hundred eighty degrees
(180.degree.) along the circumferential direction C). Consequently,
an inlet 216 of cooling channel 214 is positioned radially opposite
an outlet 218 of cooling channel 214. A first radial direction R1
extends between inlet 216 and outlet 218 of cooling channel 214 for
reference.
Inlet groove 220 is defined axially along at least a portion of
piston head 206 and along at least a portion of skirt 208 at outer
surface 228 of piston 200. Similarly, outlet groove 222 is defined
axially along at least a portion of piston head 206 and along at
least a portion of skirt 208 at outer surface 228 of piston 200.
Inlet groove 220 of piston 200 may fluidly connect an inlet passage
of casing (not shown in this embodiment) with cooling channel 214
of piston 200. Outlet groove 222 of piston 200 may fluidly connect
cooling channel 214 of piston 200 with an outlet passage of casing
(not shown in this embodiment). Accordingly, cooling fluid (e.g.,
refrigerant, oil, etc.) may flow through the inlet passage of the
casing and into inlet groove 220 of piston 200, through cooling
channel 214 of piston head 206, along outlet groove 222, and may
flow through the outlet passage of the casing where the cooling
fluid may return to a cooling fluid circuit (not shown in this
embodiment). In this manner, heat generated during the compression
process is removed from the casing and piston disposed within a
chamber of the casing. Accordingly, the discharge temperature of
the gaseous refrigerant or oil compressed within the chamber may be
reduced and a more isothermal process may be achieved, which
reduces the thermodynamic work of the compression assembly.
Cooling channel 214 is defined by piston head 206 such that it
forms a generally cylindrical cavity. Particularly, cooling channel
214 has a depth D4 (FIG. 13) that extends between a first wall 210
and second wall 212 (FIG. 12; removed in FIG. 13) of piston head
206, e.g., along the axial direction A. The depth D4 forms the
axial height or length of the cylindrical cavity of cooling channel
214. Cooling channel 214 has a base diameter BD4 (FIG. 13) that
extends between opposing sides of an inner rim 230 of piston 200.
As shown, the base diameter BD4 extends substantially all of the
radial length or diameter of piston 200, e.g., more than about
ninety percent (90%) of the radial length of piston 200.
Accordingly, the majority of first wall 210, the wall that
interacts with the hot gaseous refrigerant or oil being compressed
by piston 200 within the chamber, may be cooled by cooling fluid.
Particularly, about ninety percent (90%) or more of first wall 210
may be cooled by cooling fluid in the embodiment of FIGS. 11
through 13.
Further, as shown best in FIGS. 12 and 13, a plurality of fins 224
project from first wall 210 along the axial direction A into
cooling channel 214. Generally, fins 224 increase the surface area
in which the cooling fluid may contact and thus fins 224 increase
the heat transfer between piston 200 and the cooling fluid. For
this embodiment, fins 224 extend longitudinally along the first
radial direction R1 and are spaced from one another along a
direction perpendicular to the first radial direction R1. A first
fin 226 of fins 224 radially aligned with inlet 216 and outlet 218
has the longest radial length of fins 224 (e.g., along the first
radial direction R1). The radial length of each successive fin 224
extending outward from first fin 226 along a direction
perpendicular to the first radial direction R1 decreases. For this
embodiment, fins 224 project from first wall 210 into cooling
channel 214 a distance that is less than the depth D4. However, in
alternative embodiments, fins 224 may extend between first wall 210
and second wall 212. In some embodiments, piston 200 may be
additively manufactured, e.g., via a 3D printing process. In this
manner, fins 224 and the surfaces of piston 200 defining cooling
channel 214 may be printed having various shapes and surface
finishes, such as e.g., porous or rough surfaces.
FIG. 14 provides a close up, schematic view of a piston 320
slidably received within a chamber 312 of a casing 310 of a
compression assembly 300 according to an example embodiment of the
present subject matter. Casing 310 and piston 320 of compression
assembly 300 of FIG. 14 are similarly configured to the casing 110
and piston 120 of the linear compressor 100 of FIG. 4 except as
provided below. As shown in FIG. 14, one or more passages, grooves,
or channels may contain or receive a metallic foam component 330.
Particularly, for the embodiment of FIG. 13, metallic foam
component 330 is disposed within cooling channel 354 defined by
piston head 322 of piston 320. For this embodiment, metallic foam
component 330 fills substantially all of the volume of cooling
channel 354. Although not show, in some alternative exemplary
embodiments, metallic foam components 330 may be positioned within
inlet passage 342 and/or outlet passage 344. In yet other
embodiments, metallic foam components 330 may be positioned within
inlet groove 356 and/or outlet groove 358.
Generally, the metallic foam component 330 may facilitate removal
of the heat generated during the compression process by
facilitating the transfer of heat to the cooling fluid CF.
Particularly, the metallic foam component 330 increases the surface
area in which the cooling fluid CF may contact and thus the
metallic foam component 330 may increase the heat transfer between
the piston 320/casing 310 and the cooling fluid CF. Metallic foam
component 330 may cause the cooling fluid CF flowing through heat
exchanger 140 to exhibit a more turbulent flow, which ultimately
facilitates heat transfer to the cooling fluid CF. The metallic
foam component 330 may have a cellular structure formed of metal
with a plurality of pores.
FIG. 15 provides a schematic cross-sectional view of a piston 420
slidably received within a chamber 412 of a casing 410 of an
example compression assembly 400 according to an example embodiment
of the present subject matter. Casing 410 and piston 420 of
compression assembly 400 of FIG. 15 are similarly configured to the
casing 110 and piston 120 of the linear compressor 100 of FIG. 4
except as provided below.
As shown in FIG. 15, casing 410 defines a plurality of casing
channels, including a first casing channel 481, a second casing
channel 482, and third casing channel 483. The casing channels 481,
482, 483 are spaced from one another along the axial direction A
and each extend annularly about chamber 412 of casing 410. Further,
the casing channels 481, 482, 483 are each fluidly connected by
inlet passage 442 and outlet passage 444 at radially opposite
positions. Notably, inlet passage 442, outlet passage 444, and
casing channels 481, 482, 483 are defined by casing 110 at an outer
surface 418 of casing 410. Outer surface 418 is radially spaced
from inner surface 416 of casing 410 that defines chamber 412. As
the inlet passage 442, outlet passage 444, and casing channels 481,
482, 483 are defined at outer surface 418 of casing 410, machining
of such passages and casing channels is made easier. To enclose the
passages and casing channels, a casing cap 430 is attached to or
fit over casing 410 as shown in FIG. 15. Casing cap 430 may define
a first radial hole to define an inlet 446 of inlet passage 442 and
a second radial hole to define an outlet 452 of outlet passage
444.
Further, as depicted in FIG. 15, a plurality of fins 434 may be
machined into first wall 421 of piston head 422 and cooling channel
454 may be defined. Thereafter, a piston cap 432 may be attached to
or otherwise connected to piston 420 such that it forms second wall
423 of piston head 422 and encloses cooling channel 454. With such
an arrangement, the ease of manufacturing piston 420 is
improved.
FIG. 16 provides a schematic view of another linear compressor 500
according to an example embodiment of the present subject matter.
The linear compressor 500 of FIG. 16 is similarly configured to the
linear compressor 100 of FIG. 3 except as provided below.
For the depicted embodiment of FIG. 16, the cooling fluid circuit
530 is a closed loop circuit and is configured to receive a cooling
fluid CF, e.g., oil. Cooling fluid circuit 530 is completely
enclosed or entirely encased within hermetic shell 504, and
accordingly, any leakage of cooling fluid CF from cooling fluid
circuit 530 is contained within hermetic shell 504. Cooling fluid
circuit 530 may include a tube or conduit that is fluidly connected
with inlet 546 of inlet passage 542 of casing 510 at one end and
outlet 552 of outlet passage 544 at its other end. In some
embodiments, the cooling fluid CF circulates through cooling fluid
circuit 530 by reciprocation of piston 520 within chamber 512 of
casing 510. Cooling fluid CF may be driven through cooling fluid
circuit 530 such that heat is removed or extracted from the
relatively hot surfaces and walls of casing 510 and piston 520. In
some embodiments, advantageously, cooling fluid circuit 530 is kept
at the same elevation, e.g., along the axial direction A. Further,
for the depicted embodiment of FIG. 16, no refrigerant from the
vapor compression cycle need be routed to heat exchanger 540 of the
compressor 500.
Further, in some exemplary embodiments, a circulation device 532 is
optionally positioned along cooling fluid circuit 530, e.g., to
circulate or drive cooling fluid CF through cooling fluid circuit
530. As one example, circulation device 532 may be a pump. For
instance, the pump may be a pump positioned in an oil sump of
linear compressor 500. In some embodiments, a controller 534 is
communicatively coupled with circulation device 532, e.g., via a
suitable wired or wireless communication link. Controller 534 is
operable to control circulation device 532. For instance,
controller 534 may control circulation device 532 to increase or
decrease the flow rate of the cooling fluid CF within cooling fluid
circuit 530, e.g., based on one or more temperature signals from a
temperature sensor. Controller 534 may be similarly configured as
controller 90 of FIG. 2.
This written description uses examples to disclose the invention,
including the best mode, and also to enable any person skilled in
the art to practice the invention, including making and using any
devices or systems and performing any incorporated methods. The
patentable scope of the invention is defined by the claims, and may
include other examples that occur to those skilled in the art. Such
other examples are intended to be within the scope of the claims if
they include structural elements that do not differ from the
literal language of the claims, or if they include equivalent
structural elements with insubstantial differences from the literal
languages of the claims.
* * * * *